Rankine cycle waste heat recovery system

ABSTRACT

This disclosure relates to a waste heat recovery (WHR) system and to a system and method for regulation of a fluid inventory in a condenser and a receiver of a Rankine cycle WHR system. Such regulation includes the ability to regulate the pressure in a WHR system to control cavitation and energy conversion.

CROSS-REFERENCE TO RELATED APPLICATIONS

This application is a continuation of U.S. patent application Ser. No.13/344,261, filed Jan. 5, 2012. U.S. patent application Ser. No.13/344,261 claims the benefit of priority to U.S. Provisional PatentApplication No. 61/430,328 filed on Jan. 6, 2011, and to U.S.Provisional Patent Application No. 61/447,433, filed on Feb. 28, 2011.All of these applications are incorporated herein by reference in theirentirety.

STATEMENT REGARDING FEDERALLY SPONSORED RESEARCH OR DEVELOPMENT

This invention was made with government support under “RANKINE CYCLEWASTE HEAT RECOVERY SYSTEM,” contract number DE-FC26-05NT42419 awardedby the Department of Energy (DOE). The government has certain rights inthe invention.

TECHNICAL FIELD

This disclosure relates to a waste heat recovery (WHR) system and to asystem and method for regulation of a fluid inventory in a condenser, asub-cooler, and a receiver of a Rankine cycle WHR system.

BACKGROUND

Applying a Rankine cycle, including an organic Rankine cycle, to aninternal combustion engine may offer a fuel economy improvement bycapturing a portion of heat energy that normally would be wasted in aninternal combustion engine. However, control and operation of the systemthroughout an engine's transient duty cycle and through changingenvironments is challenging. Increasing the flexibility of operation ofa WHR system may assist operation of the WHR system through an engine'sduty cycle and through changing environments.

SUMMARY

This disclosure provides a waste heat recovery system for an internalcombustion engine comprising a working fluid circuit and a fluidmanagement system. The working fluid circuit contains a working fluidand includes a condenser/sub-cooler positioned along the working fluidcircuit. The condenser/sub-cooler contains a liquid working fluid havinga first fluid level. The working fluid circuit also includes a heatexchanger positioned along the working fluid circuit downstream of thecondenser/sub-cooler. The working fluid circuit also includes an energyconversion device positioned along the working fluid circuit between theheat exchanger and the condenser/sub-cooler. The fluid management systemincludes a receiver containing the liquid working fluid and a transfercircuit fluidly connecting the receiver and the condenser/sub-cooler.The liquid working fluid in the receiver has a second fluid level and aminimum second fluid level is higher than a maximum first fluid level. Apump is positioned along the transfer circuit between thecondenser/sub-cooler and the receiver. The waste heat recovery systemincludes at least one sensor adapted to measure a condition of theworking fluid circuit. The waste heat recovery system includes a controlmodule adapted to receive the condition signal from the at least onesensor and to generate a pump control signal based on the conditionsignal to control operation of the pump to transfer liquid working fluidbetween the receiver and the condenser/sub-cooler to change the firstfluid level.

This disclosure also provides a waste heat recovery system for aninternal combustion engine comprising a working fluid circuit and afluid management system. The working fluid circuit contains a workingfluid. The working fluid circuit includes a condenser/sub-coolerpositioned along the working fluid circuit and containing a liquidworking fluid having a first fluid level. The working fluid circuitincludes a heat exchanger positioned along the working fluid circuitdownstream of the condenser/sub-cooler. The working fluid circuitincludes an energy conversion device positioned along the working fluidcircuit between the heat exchanger and the condenser/sub-cooler. Thefluid management system includes a receiver containing the liquidworking fluid and a transfer circuit fluidly connecting the receiver andthe condenser/sub-cooler. The liquid working fluid in the receiver has asecond fluid level and a minimum second fluid level is higher than amaximum first fluid level. A pump is positioned along the transfercircuit between the condenser/sub-cooler and the receiver. A valve ispositioned along the transfer circuit between the condenser/sub-coolerand the receiver in parallel to the pump. The waste heat recovery systemcomprises at least one sensor adapted to measure a condition of theworking fluid circuit. The waste heat recovery system also comprises acontrol module adapted to receive the condition signal from the at leastone sensor to generate a pump control signal and a valve control signalbased on the condition signal to control operation of the pump and thevalve to transfer liquid working fluid between the receiver and thecondenser/sub-cooler to change the first fluid level.

This disclosure also provides a waste heat recovery system for aninternal combustion engine. The waste heat recovery system comprises aworking fluid circuit and a fluid management system. The working fluidcircuit contains a working fluid. A condenser/sub-cooler is positionedalong the working fluid circuit. The condenser/sub-cooler contains aliquid working fluid having a first fluid level. A pump is positionedalong the working fluid circuit downstream of the condenser/sub-cooler.A heat exchanger is positioned along the working fluid circuitdownstream of the pump. An energy conversion device is positioned alongthe working fluid circuit between the heat exchanger and thecondenser/sub-cooler. The fluid management system includes a bypassvalve positioned between the pump and the heat exchanger. The fluidmanagement system includes a receiver containing the liquid workingfluid positioned along the fluid management system downstream from thebypass valve, wherein the liquid working fluid in the receiver has asecond fluid level and wherein a minimum second fluid level is higherthan a maximum first fluid level. A receiver fill valve is positionedalong the fluid management system between the bypass valve and thereceiver. A fluid branch extends along the fluid management system froma location between the bypass valve and the receiver fill valve to thecondenser/sub-cooler. A check valve having a cracking pressure andpermitting flow only toward the condenser/sub-cooler is positioned alongthe fluid branch. An ejector positioned along the fluid branch betweenthe check valve and the condenser/sub-cooler. A connecting passageextending along the fluid management system from a position between thereceiver fill valve and the receiver to the ejector. A receiver drainvalve is positioned along the connecting passage. At least one sensoradapted to measure a condition of the working fluid circuit. The wasteheat recovery system also comprises a control module adapted to receivethe signal from the at least one sensor to generate at least one valvecontrol signal based on the condition signal to control operation of oneor more of the bypass valve, the receiver fill valve, and the receiverdrain valve to transfer liquid working fluid between the receiver andthe condenser/sub-cooler to change the first fluid level.

Advantages and features of the embodiments of this disclosure willbecome more apparent from the following detailed description ofexemplary embodiments when viewed in conjunction with the accompanyingdrawings.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a conventional Rankine cycle WHR system.

FIG. 2 is a WHR system in accordance with a first exemplary embodimentof the present disclosure.

FIG. 3 is a WHR system in accordance with a second exemplary embodimentof the present disclosure.

FIG. 4 is a WHR system in accordance with a third exemplary embodimentof the present disclosure.

DETAILED DESCRIPTION

FIG. 1 shows a conventional WHR system 10. System 10 includes asub-cooler 12, a receiver 14 positioned downstream from sub-cooler 12, afeed pump 16 positioned downstream from receiver 14, a heat exchanger 18positioned downstream from feed pump 16, an energy conversion device 20positioned downstream from heat exchanger 18, and a condenser 22positioned downstream from energy conversion device 20 and upstream fromsub-cooler 12.

A liquid working fluid is located within sub-cooler 12 and receiver 14.During operation, feed pump 16 pulls liquid working fluid from receiver14 and moves the liquid working fluid downstream to heat exchanger 18.Heat exchanger 18, which may be a single heat exchanger or multiple heatexchangers, accepts a stream of waste heat from various internalcombustion engine sources (not shown). If heat exchanger 18 includesmultiple heat exchangers, these heat exchangers may be in series, inparallel or a combination of series and parallel. Heat exchanger 18 mayinclude an exhaust gas recirculation (EGR) heat exchanger, an exhaustheat exchanger, a recuperator, a pre-charge air cooler, and otherinternal combustion engine heat exchangers. WHR system 10 transfers heatfrom various internal combustion engine sources to the liquid workingfluid, which causes the liquid working fluid to boil and vaporize.

The vaporized working fluid travels downstream from heat exchanger 18 toenergy conversion device 20, which may be an expander turbine or otherdevice. The vaporized working fluid cools and loses pressure duringpassage through energy conversion device 20. The vaporized working fluidtravels downstream to condenser 22. Condenser 22 may contain a pluralityof passages through which the vaporized working fluid and condensedliquid working fluid flows. A cooling medium, such as air or a fluid,flows around these passages to cause the vaporized working fluid tocondense into liquid working fluid. The liquid working fluid flowsdownstream under the force of gravity into sub-cooler 12. The liquidworking fluid may receive additional cooling in sub-cooler 12 beforeflowing to receiver 14, thus forming a closed loop.

The Rankine cycle working fluid may be a non-organic or an organicworking fluid. Some examples of the working fluid are Genetron® R-245fafrom Honeywell, Therminol®, Dowtherm J™ from Dow Chemical Co.,Fluorinol® from American Nickeloid, toluene, dodecane, isododecane,methylundecane, neopentane, octane, water/methanol mixtures, and steam.

FIG. 2 shows a first exemplary embodiment WHR system 110 of the presentdisclosure. Elements having the same number as elements in FIG. 1function as described in FIG. 1. These elements are described in thisembodiment only for the sake of clarity. WHR system 110 includes a fluidmanagement system 24, which fluidly connects to a working fluid circuit25, and a control system 30.

Working fluid circuit 25 includes condenser 22 and sub-cooler 12.Condenser 22 and sub-cooler 12 may be two separate fluidly connectedcomponents, they may be an integral unit or they may mount to a commonbase plate 48. Downstream from sub-cooler 12 and located along workingfluid circuit 25 is feed pump 16. A temperature and pressure sensor 55may be located along working fluid circuit 25 between sub-cooler 12 andpump 16. Downstream from feed pump 16 and located along working fluidcircuit 25 are a heat exchange portion 26 and an energy conversionportion 28. Downstream from energy conversion portion 28 is condenser22. Thus, working fluid circuit 25 forms a closed loop.

Heat exchange portion 26 includes heat exchanger 18 that is downstreamfrom a heat source 70 and upstream from an exit location 72. Atemperature sensor 56 may measure the temperature along the path fromheat exchanger 18 to exit location 72.

Energy conversion portion 28 includes energy conversion device 20.Energy conversion device 20 of Rankine cycle working fluid circuit 25 iscapable of producing additional work or transferring energy to anotherdevice or system. For example, energy conversion device 20 can be aturbine that rotates as a result of expanding working fluid vapor toprovide additional work, which can be fed into the engine's driveline tosupplement the engine's power either mechanically or electrically (e.g.,by turning a generator), or it can be used to power electrical devices,parasitic or a storage battery (not shown). Alternatively, the energyconversion device can be used to transfer energy from one system toanother system (e.g., to transfer heat energy from WHR system 110 to afluid for a heating system). A temperature sensor 57 may be locatedalong working fluid circuit 25 between heat exchanger portion 26 andenergy conversion portion 28.

Fluid management system 24 includes a bypass valve 58 positioned betweenpump 16 and heat exchange portion 26. Bypass valve 58 may be anysuitable type of valve capable of controlling the flow of fluid intoworking fluid circuit 25 and fluid management system 24, and morespecifically, into a bypass passage 60 of fluid management system 24.For example, bypass valve 58 may be a three-way valve movable to a firstposition permitting flow of liquid working fluid downstream to heatexchanger portion 26 while blocking flow into bypass passage 60, asecond position permitting fluid flow into bypass passage 60 whileblocking fluid flow into working fluid circuit 25, and an intermediateposition permitting some portion of fluid flow into each of workingfluid circuit 25 and bypass passage 60 of fluid management system 24.The intermediate position may be variable to control the amount of fluidflow into each of working fluid circuit 25 and bypass passage 60 offluid management system 24 to thereby control the proportion of thedownstream flow between working fluid circuit 25 and fluid managementsystem 24 based on the operating conditions of the system. Valve 58could also be multiple two-way valves, with one valve positioned alongthe working fluid circuit 25 downstream from bypass passage 60 and onevalve positioned along bypass passage 60 downstream from working fluidcircuit 25.

Bypass conduit or passage 60 extends downstream from bypass valve 58along fluid management system 24 to two branches or passages of fluidmanagement system 24. A first branch 34 extends to a receiver 32.Located along branch 34 of fluid management system 24 is a receiver fillvalve 36. A second branch 42 of fluid management system 24 extends tocondenser 22 and sub-cooler 12. Positioned along this branch are a checkvalve 64 and an ejector 44. A connecting passage 38 of fluid managementsystem 24 extends from first branch 34 in a location between receiver 32and receiver fill valve 36 to ejector 44. A receiver drain valve 40 ispositioned along connecting passage 38. A vent passage 78 connectsworking fluid circuit 25 to fluid management system 24. Morespecifically, vent passage 78 extends from an upper portion of condenser22 to an upper portion of receiver 32 to permit bi-directional flow ofvapor between condenser 22 and receiver 32, as will be described in moredetail hereinbelow. A receiver vent valve 80, which may operate as aproportional valve movable to partial open/closed positions or may bemodulated or cycled rapidly between positions, also called binaryoperation or modulation, may be positioned along vent passage 78.

Receiver 32 contains liquid working fluid having a fluid level.Sub-cooler 12 and condenser 22 also contain liquid working fluid havinga fluid level. Receiver 32 has a position where the minimum level orsurface of the liquid working fluid in receiver 32 is higher than themaximum level or surface of the liquid working fluid in condenser 22 andsub-cooler 12. Receiver 32 may be in a physical location that is higherthan condenser 22 and sub-cooler 12.

Control system 30 may receive signals from various sensors positionedabout WHR system 110 indicative of the condition of WHR system 110. Forexample, temperature and pressure sensor 55, temperature sensor 56,temperature sensor 57 and a fluid level sensor 50 positioned withcondenser 22 and sub-cooler 12 may send signals to control system 30.Control system 30 may operate certain elements of WHR system 110. Forexample, control system 30 may operate receiver fill valve 36, receiverdrain valve 40, bypass valve 58, and receiver vent valve 80. Suchoperation may be in response to signals received from the varioussensors previously described or other sensors located in working fluidcircuit 25 and fluid management system 24.

Control system 30 may include a control module 82 and a wiring harness84. Control module 82, which may be a single processor, a distributedprocessor, an electronic equivalent of a processor, or any combinationof the aforementioned elements, as well as software, electronic storage,fixed lookup tables and the like, connects to and may control certaincomponents of WHR system 110. The connection to components of WHR system110 may be through wire harness 84, though such connection may be byother means, including a wireless system. Control module 82 may be anelectronic control unit (ECU) or electronic control module (ECM) thatmonitors the performance of an associated engine (not shown) and othercomponents and conditions of a vehicle. Control module 82 may connect toand send signals to feed pump 16, receiver fill valve 36, receiver drainvalve 40, bypass valve 58, and vent valve 80. Control module 82 may alsoconnect to and receive signals from fluid level sensor 50, temperatureand pressure sensor 55, temperature sensor 56, and temperature sensor57. Control module 82 may interface with other sensors and elements todetermine whether various components of WHR system 110 are operatingsuccessfully and to operate and control WHR system 110.

Applicants recognize the importance of controlling or regulating fluidinventory in the condenser, the sub-cooler, and the receiver of a WHRsystem to control low-side pressures and feed pump cavitation duringengine operations while remaining cost effective. In addition, a liquidlevel increase in the condenser would displace and reduce the areas forvapor condensation and would raise system pressure, which in turn wouldincrease fluid sub-cooling, a condition known to cause cavitation in aRankine cycle WHR system feed pump. A Rankine cycle WHR system is alsoprone to overpressure during a hot engine shutdown event if the enginedrives the feed pump. WHR system 110 and the other exemplary embodimentsdescribed hereinbelow operate in a manner that keeps theseconsiderations productively balanced, as will be seen from the followingdescription.

WHR system 110 may operate as follows. Feed pump 16 pulls liquid workingfluid from sub-cooler 12. Feed pump 16, which may receive an operatingsignal from control module 82, pumps the liquid working fluid downstreamto bypass valve 58. The liquid working fluid flows downstream frombypass valve 58 to heat exchange portion 26 and into bypass passage 60of fluid management system 24.

Liquid working fluid enters heat exchanger 18 of heat exchange portion26. A hot fluid, such as coolant, compressed air from a turbocharger,exhaust gas, EGR gas, lubricant, and other sources of waste heat, fromheat source 70 flows through heat exchanger 18 to exit location 72. Heattransfers from the hot fluid to the liquid working fluid, causing theliquid working fluid to form a high-pressure vapor and cooling the hotfluid. The hot fluid departs heat exchanger 18 at exit location 72,which may be an exhaust system or pipe, an EGR system, or otherlocation. The vaporized working fluid flows downstream from heatexchanger 18 to energy conversion device 20 of energy conversion portion28. As the vaporized working fluid flows through energy conversiondevice 20, the pressure and the temperature of the vaporized workingfluid decrease. The vaporized working fluid flows downstream from energyconversion device 20 to condenser 22. Condenser 22 as well as sub-cooler12 may be cooled by ram air, cooling liquid or other cooling sources 52.The cooling of condenser 22 causes the vaporized working fluid tocondense, returning the vaporized working fluid to a liquid. The liquidworking fluid then flows through the force of gravity downstream tosub-cooler 12. Working fluid may receive additional cooling insub-cooler 12.

Bypass valve 58, which may operate as a proportional valve movable topartial open/closed positions or may be modulated or cycled rapidlybetween positions, also called binary operation or modulation, isadjustable by signals received from control module 82. As notedhereinabove, bypass valve 58 may direct liquid working fluid into fluidmanagement system 24, which increases or decreases flow through heatexchange portion 26 of working fluid circuit 25, which increases anddecreases the flow of cool liquid working fluid through heat exchangeportion 26 and thus through energy conversion portion 28. Decreased flowthrough working fluid circuit 25 can decrease cooling of hot fluid fromheat source 70. Decreasing cooling of hot fluid from heat source 70 maylead to benefits for an associated engine (not shown). For example, anincrease in the temperature of the hot fluid may aid in permitting anassociated engine (not shown) to come to temperature more quickly,achieving efficient operation faster. An increase in the temperature ofthe hot fluid may also be desirable for other reasons, such as filterregeneration.

Fluid that enters bypass passage 60 of fluid management system 24 flowsdownstream. From bypass passage 60, the liquid working fluid may floweither through first branch 34 to receiver fill valve 36 or throughsecond branch 42 to check valve 64. Control module 82 may control theopening and closing of receiver fill valve 36, which may operate as aproportional valve movable to partial open/closed positions or may bemodulated or cycled rapidly between positions, also called binaryoperation or modulation. When receiver fill valve 36 is open, liquidworking fluid flows downstream from receiver fill valve 36 to receiver32. When receiver fill valve 36 is closed, liquid working fluid flowsinto second branch 42 to check valve 64, which may have an opening orcracking pressure of approximately 5 PSI. The opening or crackingpressure of check valve 64 prevents low bypass flow from opening checkvalve 64. Thus, low bypass flow is capable of rising through receiverfill valve 36 when receiver fill valve 36 is open to flow to receiver32. When receiver fill valve 36 is closed, the liquid working fluid thatflows through bypass passage 60 may flow through check valve 64 if thepressure of the liquid working fluid in bypass passage 60 exceeds theopening or cracking pressure of check valve 64. The liquid working fluidthen flows downstream through ejector 44 to condenser 22 and sub-cooler12.

If control module 82 commands receiver drain valve 40 to open, receiverfill valve 36 to close, and receiver vent valve 80 to open, then bypassfluid flow through check valve 64 and ejector 44 causes reduced pressurein connecting passage 38. Drain valve 40 may operate as a proportionalvalve movable to partial open/closed positions or may be modulated orcycled rapidly between positions, also called binary operation ormodulation. The reduced pressure in connecting passage 38 causes liquidworking fluid to flow from receiver 32 through drain valve 40 and theninto ejector 44. The liquid working fluid joins the flow of liquidworking fluid flowing through second branch 42 at ejector 44, flowingdownstream to condenser 22 and sub-cooler 12, which increases or raisesthe level of fluid in condenser 22 and sub-cooler 12.

The level of the liquid working fluid inside condenser 22 and sub-cooler12 affects sub-cooling of the liquid working fluid that flows downstreamto feed pump 16. With respect to the level of the liquid working fluidin condenser 22 and sub-cooler 12, an increase in the level of theliquid working fluid increases sub-cooling. A decrease in the level ofthe liquid working fluid decreases sub-cooling. As the level of theliquid working fluid increases, the pressure in condenser 22 increasesas the relative volume between condensing and sub-cooling shifts. Theincreased pressure of the liquid working fluid as it flows toward pump16 provides benefits, which includes increasing the cavitation margin ofpump 16 by increasing the working fluid sub-cooling (the degrees oftemperature below the saturation temperature for the measured pressure),which assists pump 16 in maintaining prime, or the ability to movefluid. An increase in pressure in working fluid circuit 25 reduces thepower from energy conversion device 20 because the pressure drop acrossenergy conversion device 20 decreases, so the optimum level of theliquid working fluid in condenser 22 and sub-cooler 12 is when the levelis as low as possible without causing feed pump 16 to cavitate.

Vent passage 78 and vent valve 80, which is physically near the topportion of receiver 32, allows pressure within receiver 32 of fluidmanagement system 24 to be similar to pressure within condenser 22 ofworking fluid circuit 25 during normal operation. Vent passage 78 andvent valve 80 also allows vapor to enter or exit receiver 32 when liquidworking fluid is transferred in and out of receiver 32. Vapor that mayform within receiver 32 is able to travel through vent conduit 78 andvent valve 80 to condenser 22.

The level of liquid working fluid in condenser 22 and sub-cooler 12 maybe set by fluid level sensor 50 or by monitoring the temperature andpressure of the liquid working fluid exiting sub-cooler 12 using sensors55. For example, when the temperature and pressure signals from sensor55 to control module 82 indicate that a sub-cooling temperature,Tsub-cool, which is equal to a saturation temperature, Tsaturation,minus a measured temperature, Tmeasured, is below a target range andcavitation may occur in feed pump 16, control module 82 may send signalsto close receiver fill valve 36 and to open receiver drain valve 40 toincrease or raise the level of liquid working fluid in condenser 22 andsub-cooler 12. Liquid working fluid from bypass passage 60 may assist inincreasing the level of liquid working fluid in condenser 22 andsub-cooler 12, as has been described hereinabove. Tsaturation is a valueestablished in control module 82 for a given pressure. Tmeasured isacquired from sensors 55.

When sub-cooling, Tsub-cooling, is too high or above a target level,control module 82 may command receiver fill valve 36 to open andreceiver drain valve 40 to close, which allows liquid working fluid toflow from bypass passage 60 through check valve 64 into receiver 32. Aspreviously noted, the cracking pressure of normally closed check valve64 is such that it permits liquid working fluid to flow through receiverfill valve 36 even when pressure in bypass passage 60 is relatively low.Otherwise, check valve 64 might permit liquid working fluid to drainfrom receiver 32 into sub-cooler 12 when receiver fill valve 36 is open.

When sub-cooling, Tsub-cooling, is too low, control module 82 commandsreceiver drain valve 40 to open and receiver fill valve 36 to close,allowing liquid working fluid to flow through drain valve 40, throughejector 44 into sub-cooler and condenser 22. Ejector 44 acts like aVenturi in this situation. Liquid working fluid flowing through secondbranch 42 and through ejector 44 creates a vacuum pressure on connectingpassage 38. This vacuum pressure pulls liquid working fluid fromreceiver 32 and connecting passage 38 into ejector 44, thus making useof the potential energy of the liquid working fluid from the bypasspassage 60. The pressure of the combined fluid streams flowing throughejector 44 to condenser 22 and sub-cooler 12 is also increased.

If Tsub-cool is approximately at a target value, then any fluidtraveling into fluid management system 24 from bypass valve 58 is routeddirectly through check valve 64 to condenser 22/sub-cooler 12, whilereceiver fill valve 36 and receiver drain valve 40 are closed by signalsreceived control module 82.

Receiver vent valve 80 is normally open during operation of WHR system110, as previously described. Upon shutdown of an associated engine,control module 82 commands receiver vent valve 80 to close, receiverfill valve 36 to close, and receiver drain valve 40 to open. If WHRsystem 110 is hot, the liquid working fluid in heat exchanger 18continues to vaporize. This vapor continues to condense in condenser 22,causing condenser 22 to flood with liquid working fluid since feed pump16 is not operating upon engine shutdown. Pressure increases incondenser 22 as less volume is available for vaporized working fluid tocondense, which could lead to an overpressure condition. With receivervent valve 80 closed, the increased pressure in condenser 22 forcesliquid working fluid through ejector 44 into connecting passage 38,through open receiver drain valve 40, into first branch 34, and intoreceiver 32. By forcing liquid working fluid into receiver 32, condenser22 does not flood and its pressure remains below the design pressure ofheat exchanger 18, thus preventing an overpressure condition incondenser 22 and the other elements of working fluid circuit 25. Notethat liquid working fluid is unable to flow from condenser 22 andsub-cooler 12 through check valve 64 because check valve 64 permitsone-way operation only. Any fluid that attempts to flow through checkvalve 64 when the pressure on the downstream is higher than the upstreamside forces check valve 64 closed.

Receiver vent valve 80 may operate as a proportional valve movable topartial open/closed positions or may be modulated or cycled rapidlybetween positions, also called binary operation or modulation,controlled by control module 82, to regulate the pressure of condenser22 during operation of the Rankine cycle. As previously noted,temperature and pressure sensor 55 may send signals to control module82. If control module 82 senses a transient condition leading toincreased pressure in WHR system 110, then control module 82 may commandreceiver vent valve 80 to open or close. With receiver vent valve 80closed, increased pressure forces liquid working fluid into receiver 32,through the previously described fluid path that includes receiver drainvalve 40, equalizing pressure throughout WHR system 110. With receivervent valve 80 open, pressure is able to increase throughout the system.

Control module 82 may also adjust the superheat temperature,Tsuperheat=Tmeasured−Tsaturation, of the vaporized working fluid.Tsaturation is derived from a pressure signal control module 82 receivesfrom temperature and pressure sensor 57. Tmeasured is also a signalreceived from sensor 57. Tsuperheat has a target range. If Tsuperheat islower than the target range, control module 82 may decrease the flow ofliquid working fluid through working fluid circuit 25 by controllingbypass valve 58, reduced working fluid flow rate while at a constantwaste heat input available increases the superheat. Control module 82may also decrease sub-cooling. Control module 82 may also control theflow of waste heat to heat exchange portion 26 to increase heat transferto the liquid working fluid.

If Tsuperheat is above a target range, control module 82 may increasethe flow of working fluid through working fluid circuit 25 and mayincrease sub-cooling to decrease Tsuperheat. Control module 82 may alsodecrease the flow of waste heat through heat exchange portion 26 todecrease superheat until it reaches the target range.

FIG. 3 shows a second exemplary embodiment WHR system 210. Elementshaving the same item number as FIG. 1 and FIG. 2 function as describedin FIGS. 1 and 2. These elements are described in this embodiment onlyfor the sake of clarity. WHR system 210 includes a fluid managementsystem 124, which connects to a working fluid circuit 125. A controlsystem 130 may operate certain elements of WHR system 210.

Working fluid circuit 125 includes condenser 22, sub-cooler 12, pump 16,a heat exchange portion 126, and an energy conversion portion 128.

Sub-cooler 12 is downstream from condenser 22. Located along workingfluid circuit 125 downstream from sub-cooler 12 is pump 16. Heatexchange portion 126 is located along working fluid circuit 125downstream from pump 16. Energy conversion portion 128 is located alongworking fluid circuit 125 downstream from heat exchange portion 126 andupstream from condenser 22. Ram air or fluid 52 provides cooling tocondenser 22 and sub-cooler 12. Both sub-cooler 12 and condenser 22 maymount on base plate 48.

Fluid management system 124 includes a transfer circuit 88 and receiver32. Transfer circuit 88 is located along fluid management system 124 andconnects receiver 32 to condenser 22 and sub-cooler 12. Located alongtransfer circuit 88 is a bi-directional pump 86, which may be anelectric pump. Pump 86 is fluidly connected between receiver 32 andcondenser 22/sub-cooler 12. A vent passage 94 connects working fluidcircuit 125 to fluid management system 126. More specifically, ventpassage 94 connects to a top portion of receiver 32 and to a top portionof condenser 22.

Feed pump 16 is prone to cavitation because the liquid working fluid canoperate near the phase change point. During large heat input transientsor abrupt changes in ambient air temperature to the condenser, the fluidin the receiver may boil, reducing the ability to pump the liquidworking fluid, which reduces cooling in heat exchange portion 126. Theoperation of transfer circuit 88, and more specifically bi-directionaltransfer pump 86, assists in operating WHR system 210 near an optimaloperating point that balances cavitation and cooling capability.

Raising or increasing the level of the liquid working fluid in condenser22 and sub-cooler 12 increases the area and volume for sub-cooling,which increases sub-cooling and decreases the volume for condensation.The increase in the volume of liquid working fluid increases pressure incondenser 22, which decreases the likelihood of cavitation in pump 16and improves the ability to pump the liquid working fluid. However,raising the level of the liquid working fluid also decreases the turbinepower due to increased condenser pressure.

During a large engine transient or temperature change of ram air orcooling liquid 52, condenser 22 pressure may drop rapidly, causing theliquid working fluid in sub-cooler 12 to approach saturation, meaningthat the liquid working fluid nears the phase change point where theliquid working fluid is close to vaporizing. Because the liquid workingfluid is close to saturation, the action of feed pump 16 may cause theliquid working fluid to vaporize locally, causing cavitation in feedpump 16. Such cavitation is undesirable because it may cause damage tofeed pump 16 as well as pressuring WHR system 210 in an undesirablelocation.

Control system 130 may include a control module 182 and a wiring harness184. Control module 182, which may be a single processor, a distributedprocessor, an electronic equivalent of a processor, or any combinationof the aforementioned elements, as well as software, electronic storage,fixed lookup tables and the like, connects to and may control certaincomponents of WHR system 210. The connection to components of WHR system210 may be through wire harness 184, though such connection may be byother means, including a wireless system. Control module 182 may be anelectronic control unit (ECU) or electronic control module (ECM) thatmonitors the performance of an associated engine (not shown) and othercomponents and conditions of a vehicle.

Control module 182 receives temperature and pressure signals from sensor55, a temperature signal from sensor 56, a temperature and pressuresignals from sensor 57, and a fluid level signal from fluid level sensor50 that indicate the status of the liquid working fluid. For example,the temperature and pressure measured by sensor 55 may indicate that asub-cooling temperature, Tsub-cool, which is equal to a saturationtemperature, Tsaturation, minus a measured temperature, Tmeasured, isbelow a target range. Temperature sensor 56 may indicate a need tochange cooling of fluid from heat source 70. Temperature sensor 57 mayindicate a need to increase or decrease the superheat temperature of thevaporized working fluid.

To prevent undesirable cavitation, control module 182 may controltransfer pump 86 of transfer circuit 88 to transfer liquid working fluidfrom receiver 32 into condenser 22 and sub-cooler 12. Vaporized workingfluid is able to flow from condenser 22 through vent passage 94 towardreceiver 32 to permit the liquid working fluid to flow from receiver 32.The pressure in condenser 22 increases with the increased level of theliquid working fluid and sub-cooling increases to the minimum requiredlevel, which moves the liquid working fluid in condenser 22 andsub-cooler 12 away from the saturation point.

Conditions in condenser 22 and sub-cooler 12 may also lead to anincrease in condenser 22 pressure. For example, if the liquid workingfluid level increases beyond an optimal level, power from energyconversion portion 128 or from energy conversion device 20 may fallbelow a useful or desirable level because the pressure differentialacross energy conversion device 20 decreases. As before, the pressureand temperature signal from sensor 55 and from fluid level sensor 50 mayindicate that the level of the liquid working fluid is higher thandesirable, leading to sub-cooling higher than a target level. In thiscircumstance, control module 182 may control transfer pump 86 oftransfer circuit 88 to move liquid working fluid from condenser 22 andsub-cooler 12 to receiver 32. As liquid working fluid flows intoreceiver 32, vaporized working fluid flows from receiver 32 through ventconduit 92 into condenser 22, preventing undesirable pressurization ofliquid working fluid in receiver 32. The result is that the level of theliquid working fluid in condenser 22 and sub-cooler 12 decreases,thereby decreasing the pressure of the vaporized working fluid incondenser 22, which increases the power from energy conversion device 20since the pressure differential across energy conversion device 20increases.

FIG. 4 shows a third exemplary embodiment WHR system 310. Items have thesame number as items in FIGS. 1, 2 and 3 operate in a manner similar tothose items and descriptions of previously described items are forclarity only.

WHR system 310 includes a fluid management system 224, which connects toa working fluid circuit 125. A control system 230 may operate certainelements of WHR system 210.

WHR system 310 includes a fluid management system 224, which connects toworking fluid circuit 125. Working fluid circuit 125 includes condenser22, sub-cooler 12, pump 16, heat exchange portion 126, and energyconversion portion 128. Located along working fluid circuit 125downstream from sub-cooler 12 is pump 16. Located along working fluidcircuit 125 downstream from pump 16 is heat exchange portion 126.Downstream from heat exchange portion 126 and located along workingfluid circuit 125 is energy conversion portion 128. Energy conversionportion 128 connects to an upstream side of condenser 22. Control system230 may operate certain elements of WHR system 310. Ram air or fluid 52provides cooling to condenser 22 and sub-cooler 12. Both sub-cooler 12and condenser 22 may mount on base plate 48.

Fluid management system 224 includes receiver 32 and a transfer circuit188. Transfer circuit 188 is located along fluid management system 224and connects receiver 32 to condenser 22/sub-cooler 12. Transfer circuit188 includes a transfer pump 96 and a drain valve 106. Transfer pump 96is located along transfer circuit 188 between receiver 32 and condenser22/sub-cooler 12. Drain valve 106 is also located along transfer circuit188 between receiver 32 and condenser 22/sub-cooler 12 in a positionparallel to transfer pump 96. Transfer pump 96 may be an electric pump.Vent passage 94 connects working fluid circuit 125 to fluid managementsystem 126. More specifically, vent passage 94 connects to a top portionof receiver 32 and to a top portion of condenser 22.

Feed pump 16 is prone to cavitation because the liquid working fluid canoperate near the phase change point. During large heat input transientsor abrupt changes in ambient air temperature to the condenser, the fluidin the receiver may boil, reducing the ability to pump the liquidworking fluid, which reduces cooling in heat exchange portion 126. Theoperation of transfer circuit 188 assists in operating WHR system 310near an optimal operating point that balances cavitation and coolingcapability.

Raising or increasing the level of the liquid working fluid in condenser22 and sub-cooler 12 increases the area and volume for sub-cooling anddecreases the volume for condensation. The increase in the volume ofliquid working fluid increases sub-cooling. The increase in the volumeof liquid working fluid decreases the likelihood of cavitation in pump16 and improves the ability to pump the liquid working fluid. However,raising the level of the liquid working fluid also decreases power fromenergy conversion device 20 due to increased pressure in condenser 22,which decreases the pressure drop across energy conversion device 20.

During a large engine transient or temperature change of ram air orcooling liquid 52, the pressure in condenser 22 may drop rapidly,causing the liquid working fluid in sub-cooler 12 to approachsaturation, meaning that the liquid working fluid nears the phase changepoint where the liquid working fluid is close to vaporizing. Because theliquid working fluid is close to saturation, the action of feed pump 16may cause the liquid working fluid to vaporize locally, causingcavitation in feed pump 16. Such cavitation is undesirable because itmay cause damage to feed pump 16 as well as pressurizing WHR system 210in an undesirable location.

Control system 230 may include a control module 282 and a wiring harness284. Control module 282, which may be a single processor, a distributedprocessor, an electronic equivalent of a processor, or any combinationof the aforementioned elements, as well as software, electronic storage,fixed lookup tables and the like, connects to and may control certaincomponents of WHR system 310. The connection to components of WHR system310 may be through wire harness 284, though such connection may be byother means, including a wireless system. Control module 282 may be anelectronic control unit (ECU) or electronic control module (ECM) thatmonitors the performance of an associated engine (not shown) and othercomponents and conditions of a vehicle.

Control module 282 receives temperature and pressure signals from sensor55, a temperature signal from sensor 56, a temperature and a pressuresignal from sensor 57, and a fluid level from fluid level sensor 50 thatindicate the status of the liquid working fluid. For example, thetemperature and pressure measured by sensor 55 may indicate that asub-cooling temperature, Tsub-cool, which is equal to a saturationtemperature, Tsaturation, minus a measured temperature, Tmeasured, isbelow a target range. Temperature sensor 56 may indicate a need tochange cooling of fluid from heat source 70. Temperature and pressuresensor 57 may indicate a need to increase or decrease the superheattemperature of vaporized working fluid.

To prevent undesirable cavitation, control module 282 may control drainvalve 106 of transfer circuit 188 to transfer liquid working fluid fromreceiver 32 downstream into condenser 22 and sub-cooler 12. Drain valve106 may operate as a proportional valve movable to partial open/closedpositions or may be modulated or cycled rapidly between positions, alsocalled binary operation or modulation. Vaporized working fluid is ableto flow from condenser 22 through vent passage 94 toward receiver 32 topermit the liquid working fluid to flow from receiver 32. Duringtransfer of liquid working fluid from receiver 32 to condenser22/sub-cooler 12, control module 282 may command transfer pump 96 to bein an “off” or non-operating mode. The pressure in condenser 22increases with the increased level of the liquid working fluid andsub-cooling increases to the minimum required level, which increases thesub-cooling of the liquid working fluid in condenser 22 and sub-cooler12 toward a target range.

Conditions in condenser 22 and sub-cooler 12 may also lead to anincrease in condenser 22 pressure, which increases sub-cooling. Forexample, if the liquid working fluid level increases beyond an optimallevel, power from energy conversion portion 128 or from energyconversion device 20 may fall below a useful or desirable level becausethe pressure differential across energy conversion device 20 decreases.The pressure and temperature signal from sensor 55 and from fluid levelsensor 50 may indicate that sub-cooling is higher than desirable. Inthis circumstance, control module 282 may control transfer pump 96 oftransfer circuit 188 to move liquid working fluid from condenser22/sub-cooler 12 downstream to receiver 32. Control module 282 closesdrain valve 106 during the transfer of fluid from Condenser 22 andsub-cooler 12 to receiver 32. Vaporized working fluid flows fromreceiver 32 through vent passage 94 into condenser 22, preventingundesirable pressurization of liquid working fluid in receiver 32. Theresult is that the level of the liquid working fluid in condenser 22 andsub-cooler 12 decreases, thereby decreasing the pressure of thevaporized working fluid in condenser 22 and decreasing sub-cooling,which increases the power from energy conversion device 20 since thepressure differential across energy conversion device 20 increases.

While various embodiments of the disclosure have been shown anddescribed, it is understood that these embodiments are not limitedthereto. The embodiments may be changed, modified and further applied bythose skilled in the art. Therefore, these embodiments are not limitedto the detail shown and described previously, but also include all suchchanges and modifications.

What is claimed is:
 1. A method of generating energy from an internalcombustion engine, the method comprising: pumping a liquid working fluidfrom a condenser to at least one valve positioned downstream of thecondenser; moving the at least one valve to a first position from asecond position, the first position permitting flow of the liquidworking fluid to a heat exchanger positioned downstream of the at leastone valve and blocking a receiver positioned downstream of the at leastone valve, the second position permitting flow of the liquid workingfluid to the receiver and blocking the heat exchanger; receiving a firstportion of the liquid working fluid at the heat exchanger; receiving awaste heat fluid from the internal combustion engine at the heatexchanger; causing heat transfer from the waste heat fluid to the firstportion of the liquid working fluid; and generating energy from thefirst portion of the liquid working fluid.
 2. The method of claim 1,further comprising: moving the at least one valve from the firstposition to the second position; and receiving a second portion of theliquid working fluid at the receiver from the at least one valve.
 3. Themethod of claim 1, wherein the at least one valve includes a three wayvalve.
 4. The method of claim 1, further comprising moving the at leastone valve from one of the first position and the second position to athird position, the third position permitting flow of the liquid workingfluid to the heat exchanger and the receiver.
 5. The method of claim 1,wherein generating energy from the first portion of the liquid workingfluid includes rotating a turbine.
 6. The method of claim 1, whereingenerating energy from the first portion of the liquid working fluidincludes generating electricity.
 7. The method of claim 1, whereingenerating energy from the first portion of the liquid working fluidincludes rotating a driveline coupled to the internal combustion engine.8. The method of claim 1, wherein the condenser includes a sub-cooler.9. The method of claim 1, wherein receiving the waste heat fluid fromthe internal combustion engine includes receiving recirculated exhaustgas.
 10. The method of claim 1, further comprising moving the at leastone valve to the first position from the second position in response tosensing a temperature of the liquid working fluid.
 11. The method ofclaim 1, wherein the at least one valve is moved from the first positionto the second position in response to receipt of a control signal from acontroller communicably coupled to the at least one valve.
 12. Aninternal combustion engine system comprising: a condenser including aliquid working fluid; a first pump fluidly coupled to the condenserdownstream of the condenser so as to receive at least a portion of theliquid working fluid from the condenser; a heat exchanger fluidlycoupled to the first pump downstream of the condenser so as to receivethe at least a portion of the liquid working fluid from the first pump,the heat exchanger including a waste heat fluid circuit; an internalcombustion engine fluidly coupled to the waste heat fluid circuit of theheat exchanger; an energy conversion device fluidly coupled to the heatexchanger so as to receive the at least a portion of the liquid workingfluid from the heat exchanger; a second pump fluidly coupled to thecondenser upstream of the condenser, the second pump configured forbi-directional pumping; and a receiver container fluidly coupled to thecondenser upstream of the second pump and the condenser, wherein thebi-directional pump is configured to transfer the liquid working fluidbetween the receiver and the condenser.
 13. The system of claim 12,further comprising a temperature sensor positioned between the firstpump and the condenser, the temperature sensor configured to sense atemperature of the liquid working fluid.
 14. The system of claim 13,further comprising a controller communicably coupled to the temperaturesensor and the second pump, the controller configured to activate thesecond pump in response to the temperature of the liquid working fluid.15. The system of claim 12, wherein the internal combustion engine isfluidly coupled to the waste heat fluid circuit of the heat exchangervia an exhaust gas recirculation line.
 16. The system of claim 12,wherein the condenser includes a sub-cooler.
 17. A method of generatingenergy from an internal combustion engine, the method comprising:pumping, via a first pump positioned upstream of the condenser, a firstportion of a liquid working fluid to the condenser from a receivercontainer positioned upstream of the condenser pumping, via a secondpump positioned downstream of the condenser, a second portion of theliquid working fluid from the condenser to at least one heat exchangerpositioned downstream of the condenser; receiving a waste heat fluidfrom the internal combustion engine at the heat exchanger; causing heattransfer from the waste heat fluid to the first portion of the liquidworking fluid; and generating energy from the first portion of theliquid working fluid.
 18. The method of claim 17, wherein pumping, viathe first pump, the first portion of the liquid working fluid to thecondenser from the receiver container is responsive to sensing atemperature of the liquid working fluid between the second pump and thecondenser.
 19. The method of claim 17, wherein generating energy fromthe first portion of the liquid working fluid includes generatingelectricity.
 20. The method of claim 17, wherein generating energy fromthe first portion of the liquid working fluid includes rotating aturbine.